Hydraulic clutch and motorcycle

Abstract

The hydraulic clutch comprises an outer cover, a center sleeve, a pressing plate, a driving friction plate, a driven friction plate and a hydraulic system, and the driving friction plate and the driven friction plate are distributed on the outer circumference of the center sleeve or / and the pressing plate. The inner diameters of part of the driving friction plates and the driven friction plates are different to adapt to different radial sizes of the center sleeve or / and the pressing plate, the first driving friction plates are distributed corresponding to the center sleeve in the axial direction, the second driving friction plates are distributed corresponding to the pressing plate in the axial direction, the bearing torque of the clutch can be controlled, and according to the requirements of different working conditions, the clutch can be controlled. The clutch is accurately controlled; a shaft-shaped group part is further formed around a piston part formed on the pressing plate, the shaft-shaped group part is sleeved with the center sleeve transmission shaft section, a pressing plate annular groove is formed in the end of the pressing plate transmission shaft section, and the center sleeve transmission shaft section extends into the pressing plate annular groove, so that the connecting strength is enhanced, the overall size is reduced, and the purpose of compact structure is achieved. And the method has relatively high economical efficiency.

Description

Technical Field

[0001] The present invention relates to the technical field of motorcycle engines, and in particular to a hydraulic clutch and a motorcycle. Background Art

[0002] The clutch is an important component of a motorcycle engine. It is usually installed between the engine and the transmission, allowing the engine and transmission to gradually engage to ensure a smooth start of the motor vehicle. It also has the characteristics of reducing the impact during gear shifting and separating the engine and transmission during emergency braking to prevent overload of the transmission system such as the transmission. With the increasing demand for automatic transmission in motorcycles, the traditional centrifugal automatic clutch and the ordinary closed clutch, the former relies on centrifugal force to engage, with a long transition time and low power transmission, and the latter relies on spring force to engage. Both types of clutches have large structures and complex operations, and are not suitable for the requirements of automatic transmission, thus promoting the development of hydraulic clutch technology.

[0003] The existing hydraulic clutch uses a hydraulic drive form to control the separation and engagement of the clutch, which is labor-saving and convenient, but also has many shortcomings. For example, the safety factor of the existing transmission clutch is only achieved by the spring compression force, and it cannot actively adjust the clutch's load torque according to actual working conditions, and its adaptability is poor; it cannot accurately control the clutch's engagement, separation and semi-clutch conditions according to actual needs, resulting in limited smoothness and response speed of power transmission, affecting the riding experience; at the same time, the overall volume is large, and the space layout is not compact enough, which limits its application in compact space scenarios.

[0004] Therefore, it is necessary to improve the structure of the hydraulic clutch in the existing technology, which can not only control the load-bearing torque of the clutch and accurately control the clutch according to the requirements of different working conditions, but also optimize the structure of related components, effectively lubricate the corresponding components in the clutch, and reduce the overall volume to achieve the purpose of compact structure and high economy. Summary of the Invention

[0005] In view of this, the object of the present invention is to provide a hydraulic clutch and a motorcycle, which can not only control the load-bearing torque of the clutch and accurately control the clutch according to the requirements of different working conditions, but also optimize the structure of related components, effectively lubricate the corresponding parts in the clutch, and reduce the overall volume to achieve the purpose of compact structure, with high economy.

[0006] To achieve the purpose of the invention, the present invention provides a hydraulic clutch, comprising an outer cover, a center sleeve, a pressure plate, a plurality of active friction plates, a plurality of driven friction plates and a hydraulic system, wherein the active friction plates and the driven friction plates are distributed on the outer circumference of the corresponding positions of the center sleeve and / or the pressure plate, and the inner diameters of the active friction plates are respectively adapted to the radial dimensions of the corresponding positions of the center sleeve and / or the pressure plate, so that the inner diameters of the several active friction plates are different; the inner diameters of the driven friction plates are respectively adapted to the radial dimensions of the corresponding positions of the center sleeve and / or the pressure plate, so that the inner diameters of the several driven friction plates are different.

[0007] Furthermore, the active friction plates include several first active friction plates and several second active friction plates, the first active friction plates are distributed axially corresponding to the center sleeve, the second active friction plates are distributed axially corresponding to the pressure plate, and the inner diameters of the first active friction plates and the second active friction plates are different.

[0008] Furthermore, the driven friction plates include a plurality of first driven friction plates and a plurality of second driven friction plates, the first driven friction plates are axially distributed corresponding to the center sleeve and are matched with the center sleeve in transmission, the second driven friction plates are axially distributed corresponding to the pressure plate and are matched with the pressure plate in transmission, and the inner diameters of the first driven friction plates and the second driven friction plates are different.

[0009] Furthermore, the center sleeve includes a center sleeve cover and a center sleeve transmission shaft section, a center sleeve step shaft is formed between the center sleeve cover and the center sleeve transmission shaft section, the inner diameter of the first active friction plate is slightly larger than the outer diameter of the center sleeve step shaft, and the first driven friction plate has an internal spline and cooperates with the keyway of the center sleeve transmission shaft section through the internal spline.

[0010] Furthermore, the pressure plate includes a pressure plate cover and a pressure plate transmission shaft section, a pressure plate step shaft is formed between the pressure plate cover and the pressure plate transmission shaft section, the inner diameter of the second active friction plate is slightly larger than the outer diameter of the pressure plate step shaft, and the second driven friction plate has an internal spline and cooperates with the keyway of the pressure plate transmission shaft section through the internal spline.

[0011] Furthermore, the hydraulic system includes a hydraulic cylinder body, the hydraulic cylinder body forms a hydraulic cylinder, and the pressure plate forms a piston portion that cooperates with the hydraulic cylinder.

[0012] Furthermore, it also includes a main shaft, the hydraulic cylinder body has a side wall, a cylinder body center sleeve and a bottom, the cylinder body center sleeve is outermost on the main shaft, the piston part is located between the side wall and the cylinder body center sleeve and forms a sliding seal, and a sliding seal is formed between the outer circle of the cylinder body and the inner circle of the pressure plate transmission shaft section.

[0013] Furthermore, a hydraulic oil passage is provided on the main shaft, and the hydraulic cylinder is connected to the hydraulic oil passage through an oil hole on the central shaft sleeve of the cylinder body;

[0014] The piston portion is provided with an annular groove, and the side wall of the hydraulic cylinder body is located in the annular groove and forms a sliding seal with the outer wall of the annular groove.

[0015] Furthermore, the pressure plate is located around the piston portion to form a shaft-shaped group of parts, and the center sleeve transmission shaft section is externally mounted on the shaft-shaped group of parts;

[0016] A pressing plate annular groove is formed at the end of the pressing plate transmission shaft section, and the center sleeve transmission shaft section extends into the pressing plate annular groove.

[0017] The motorcycle of the present invention comprises the hydraulic clutch.

[0018] Beneficial effects of the present invention: A hydraulic clutch and motorcycle of the present invention include an outer cover, a center sleeve, a pressure plate, an active friction plate, a driven friction plate and a hydraulic system, the active friction plate and the driven friction plate are distributed on the outer circumference of the center sleeve and / or the pressure plate, the inner diameters of some active friction plates and driven friction plates are different to adapt to the different radial dimensions of the center sleeve and / or the pressure plate, the first active friction plate is distributed axially corresponding to the center sleeve, and the second active friction plate is distributed axially corresponding to the pressure plate, which can control the load-bearing torque of the clutch and accurately control the clutch according to the requirements of different working conditions; an axial group portion is also formed around the piston portion formed on the pressure plate, the center sleeve transmission shaft section is outermostly fitted with the axial group portion, a pressure plate annular groove is provided at the end of the pressure plate transmission shaft section, and the center sleeve transmission shaft section extends into the pressure plate annular groove, which not only enhances the connection strength, but also reduces the overall volume, thereby achieving the purpose of compact structure and having higher economy. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 A longitudinal sectional view of the hydraulic clutch of the present invention;

[0020] Figure 2 Schematic diagram of the structure of the center sleeve;

[0021] Figure 3 It is a structural diagram of the pressing plate;

[0022] Figure 4 It is a structural diagram of the hydraulic cylinder body;

[0023] Figure 5 Schematic diagram of the structure of the first driven friction plate;

[0024] Figure 6 Schematic diagram of the structure of the second driven friction plate;

[0025] Figure 7A schematic diagram showing the structure for optimizing the size of the piston and hydraulic cylinder body;

[0026] Figure 8 This is a structural diagram showing the piston being adjusted to the outside of the hydraulic cylinder body;

[0027] Figure 9 This is a schematic diagram of the connection between the center sleeve and the coil spring after removing the spring support seat.

[0028] Explanation of the reference numerals: 1. Outer cover; 2. Center sleeve; 201. Center sleeve cover; 202. Center sleeve transmission shaft section; 203. Center sleeve stepped shaft; 3. Hexagonal nut; 4. Oil seal; 5. Bearing; 6. Main shaft; 601. Hydraulic oil channel; 602. Lubricating oil channel; 7. Sealing ring; 8. Circlip; 9. Spring seat; 10. Spring support seat; 11. Coil spring; 12. Pressure plate; 1201. Pressure plate cover; 1202. Pressure plate transmission shaft section; 1203. Pressure plate stepped shaft; 1204. Piston Part; 1205, annular groove; 1206, axial group; 1207, pressure plate annular groove; 13, first active friction plate; 14, first driven friction plate; 1401, internal spline of first driven friction plate; 15, hydraulic cylinder body; 1501, side wall of hydraulic cylinder body; 1502, cylinder body center shaft sleeve; 1503, bottom of hydraulic cylinder body; 1504, oil hole on cylinder body center shaft sleeve; 16, second active friction plate; 17, second driven friction plate; 1701, internal spline of second driven friction plate. DETAILED DESCRIPTION

[0029] The following is combined with Figure 1-9 The present invention is described in further detail.

[0030] An embodiment of the present invention discloses a hydraulic clutch, comprising an outer cover 1, a center sleeve 2, a pressure plate 12, a plurality of active friction plates, a plurality of driven friction plates, and a hydraulic system. The active friction plates and the driven friction plates are distributed on the outer circumference of the corresponding positions of the center sleeve 2 and / or the pressure plate 12. The inner diameters of the active friction plates are respectively adapted to the radial dimensions of the corresponding positions of the center sleeve 2 and / or the pressure plate 12, so that the inner diameters of the active friction plates are different; the inner diameters of the driven friction plates are respectively adapted to the radial dimensions of the corresponding positions of the center sleeve 2 and / or the pressure plate 12, so that the inner diameters of the driven friction plates are different, such as Figure 1As shown, the inner diameters of some of the active friction plates and the driven friction plates are adapted to the radial dimensions of the center sleeve 2, and the inner diameters of some of the active friction plates and the driven friction plates are adapted to the radial dimensions of the pressure plate 12. Since the radial dimensions of the center sleeve 2 are different from the radial dimensions of the pressure plate 12, the inner diameters of some of the active friction plates and the driven friction plates are different, which can flexibly adapt to shaft segments of different diameters, such as a stepped shaft structure. There is no need to replace the friction plate assembly as a whole due to changes in the radial dimensions of the components, which expands the applicability of the clutch and is suitable for transmission environments with multiple diameter differences. With the help of a differentiated radial dimension design, the active friction plates and the driven friction plates can fit tightly to the outer circumference of the center sleeve 2 and / or the pressure plate 12, realizing a reasonable arrangement of multiple layers of friction plates in a limited space, reducing radial redundant space, making the overall structure of the clutch more compact, and saving installation space. ; The adaptability of the inner diameter of the friction plate to the radial size of the corresponding component is improved, which can ensure the concentricity and contact accuracy between the friction plate and the center sleeve 2 and the pressure plate 12, reduce the eccentric wear, slippage or vibration problems caused by size mismatch, improve the stability of power transmission, and reduce mechanical loss and failure risks; Configuring friction plates with corresponding inner diameters for shaft sections with different radial sizes can make the force-bearing area of ​​each friction plate more matched with the load requirements of the position, such as large diameter sections corresponding to large inner diameter friction plates to withstand greater torque, avoid local overload or uneven wear, balance the loss rate of each friction plate, and extend the overall service life; the close adaptation of the friction plate and the component can ensure that the pressure applied by the hydraulic system is more evenly transmitted to the friction surface, reduce pressure loss, improve the response speed and control accuracy of the clutch action, make the engagement and separation process smoother, and improve transmission efficiency. I will not go into details here.

[0031] In this embodiment, the active friction plate includes a plurality of first active friction plates 13 and a plurality of second active friction plates 16. The first active friction plates 13 are distributed axially corresponding to the center sleeve 2, and the second active friction plates 16 are distributed axially corresponding to the pressure plate 12. The inner diameters of the first active friction plates 13 and the second active friction plates 16 are different. The inner diameters of the first active friction plates 13 and the second active friction plates 16 respectively match the radial dimensions of the center sleeve 2 and the pressure plate 12, and can form a tight fit with the outer circumferential surfaces of the two. This corresponding size adaptation can avoid the gap or interference problem caused by the mismatch between the inner diameter of the friction plate and the radial dimension of the mounting component, ensure the axial positioning accuracy of the active friction plate, reduce radial shaking or eccentric wear during operation, and improve the stability of the overall assembly; the center sleeve 2 and the pressure plate 12 are the core force-bearing components of the clutch, and their radial size differences usually correspond to different load transmission requirements. For example, the center sleeve 2 is connected to the input shaft, and the pressure plate 12 is associated with related actuators. The torques or radial forces borne by the two are different. Through differentiated inner diameter designs, According to the design, the first active friction plate 13 and the second active friction plate 16 can respectively form a more reasonable contact area with the corresponding components, so that the distribution of friction force in different shaft sections matches the actual load requirements, avoiding local overload, reducing the risk of slippage or friction plate damage, and improving the reliability of power transmission; the differentiated inner diameter design can directly adapt to mounting surfaces of different sizes, eliminating redundant positioning components, reducing the axial or radial space occupied by the clutch, improving space utilization, and achieving a compact structure; the first active friction plate 13 and the second active friction plate 16 correspond to the working environment of the center sleeve 2 and the pressure plate 12 respectively. The inner diameter adaptation ensures that both are in the best friction state, avoiding local wear of the small inner diameter friction plate on the large-sized component due to edge contact, or slipping wear of the large inner diameter friction plate on the small-sized component due to loose fit. This balanced wear design can extend the service life of a single set of friction plates, reduce replacement frequency, and reduce maintenance costs; the close fit between the friction plate and the mounting component ensures that the axial pressure applied by the hydraulic system is more evenly transmitted to the friction surface, reducing pressure loss caused by clearance. Especially during the clutch engagement and disengagement process, the differentiated inner diameter design enables the first active friction plate 13 and the second active friction plate 16 to respond synchronously to hydraulic control, avoiding action delays caused by size mismatch and improving the clutch control sensitivity. I will not go into details here.

[0032] In this embodiment, the driven friction plate includes a plurality of first driven friction plates 14 and a plurality of second driven friction plates 17. The first driven friction plates 14 are distributed axially corresponding to the center sleeve 2 and are in transmission cooperation with the center sleeve 2. The second driven friction plates 17 are distributed axially corresponding to the pressure plate 12 and are in transmission cooperation with the pressure plate 12. The inner diameters of the first driven friction plates 14 and the second driven friction plates 17 are different. The first driven friction plates 14 are in transmission cooperation with the center sleeve 2, and the second driven friction plates 17 are in transmission cooperation with the pressure plate 12. The inner diameters of the two respectively match the radial dimensions of the corresponding components, which can ensure the circumferential transmission structure between the driven friction plates and the mounting components, such as through splines or keyways. Precise engagement, this exclusive adaptation design can avoid transmission clearance or jamming caused by size mismatch, reduce torque loss during power transmission, and improve transmission efficiency; the center sleeve 2 and the pressure plate 12 have different functions in the clutch, and their radial size differences often correspond to different load requirements. The first driven friction plate 14 and the second driven friction plate 17 are designed with differentiated inner diameters to match their own force-bearing area with the load characteristics of the corresponding shaft section. For example, a large inner diameter driven friction plate is adapted to a large diameter shaft section to withstand higher loads, avoid local stress concentration, reduce the risk of deformation or fracture due to overload, and extend the service life of transmission components; the differentiated inner diameter design allows the driven friction plate to directly fit the corresponding The outer circumference of the component does not require redundant positioning parts, and the multi-layer friction plates are tightly arranged in the axial direction, which significantly reduces the overall volume of the clutch; the precise adaptation of the inner diameter of the driven friction plate to the corresponding component can ensure the concentricity of the two, and avoid oblique contact or partial contact between the friction plate and the active friction plate due to eccentricity during operation. This design can make the friction surface more evenly stressed, reduce abnormal wear, and at the same time reduce vibration and noise caused by uneven friction, thereby improving the smoothness of the clutch operation; during assembly, there is no need to perform additional processing on the center sleeve 2 or the pressure plate 12 to unify the inner diameter, nor is there any need to match small-sized components with gaskets and other assemblies. The driven friction plate can be directly installed according to the corresponding size, thereby improving assembly efficiency. During maintenance, the worn first driven friction plate 14 and second driven friction plate 17 can be replaced in a targeted manner without replacing the entire plate, thereby reducing spare parts consumption and maintenance time and lowering overall costs; the inner diameters of the first active friction plate 13 and the first driven friction plate 14, and the second active friction plate 16 and the second driven friction plate 17 respectively correspond to each other, which can ensure the contact synchronization of the friction surfaces of the active friction plate and the driven friction plate during the engagement and separation process, and reduce the phenomenon of partial contact first and partial contact later due to size misalignment. This collaborative design can convert the pressure of the hydraulic system into friction force more efficiently, improve the response speed and control accuracy of the clutch action, and make power switching faster and smoother. I will not go into details here.

[0033] In this embodiment, the center sleeve 2 includes a center sleeve cover 201 and a center sleeve transmission shaft section 202, and a center sleeve stepped shaft 203 is formed between the center sleeve cover 201 and the center sleeve transmission shaft section 202. The inner diameter of the first active friction plate 13 is slightly larger than the outer diameter of the center sleeve stepped shaft 203, and the first driven friction plate 14 has an internal spline 1401 and cooperates with the keyway of the center sleeve transmission shaft section 202 through the internal spline 1401. The center sleeve stepped shaft 203 serves as an axial positioning reference, and its outer diameter forms a clearance fit slightly larger than the inner diameter of the first active friction plate 13, which not only avoids unclear separation caused by interference fit, but also limits the axial movement of the first active friction plate 13 through the step surface to ensure that it is stably distributed in the corresponding shaft section. At the same time, the first driven friction plate 14 cooperates with the keyway of the center sleeve transmission shaft section 202 through the internal spline 1401 to achieve circumferential fixation while being able to move flexibly in the axial direction with the clutch action to avoid the friction plate being unable to separate; the inner diameter of the first active friction plate 13 is slightly larger than the center sleeve The outer diameter of the core sleeve stepped shaft 203 ensures that the clutch is completely disengaged, and the standardized fit between the internal spline 1401 of the first driven friction plate 14 and the keyway of the center sleeve transmission shaft segment 202 can achieve rapid alignment installation through the guidance of the spline, reducing assembly time and errors and improving assembly efficiency; the clearance fit between the first active friction plate 13 and the center sleeve stepped shaft 203 ensures that there is no direct friction with the surface of the shaft segment when it rotates with the active component, avoiding energy loss and heat caused by contact wear. At the same time, the internal spline fit of the first driven friction plate 14 is a rigid transmission, ensuring efficient torque transmission. The two have a clear division of labor and reduce ineffective energy consumption; the design of the center sleeve stepped shaft 203 causes the shaft segment diameter to form a gradient change. Compared with the equal-diameter shaft segment, the structural strength can be improved by increasing the diameter in the stress concentration area to resist the radial bending moment caused by the axial pressure of the friction plate. At the same time, the step structure provides additional support for the shaft segment, reduces vibration during high-speed rotation, and improves the stability of the clutch under high-speed and high-torque conditions.

[0034] In this embodiment, the pressure plate 12 includes a pressure plate cover 1201 and a pressure plate transmission shaft section 1202, a pressure plate step shaft 1203 is formed between the pressure plate cover 1201 and the pressure plate transmission shaft section 1202, the inner diameter of the second active friction plate 16 is slightly larger than the outer diameter of the pressure plate step shaft 1203, the second driven friction plate 17 has an internal spline 1701 and cooperates with the keyway of the pressure plate transmission shaft section 1202 through the internal spline 1701, and the stepped structure of the pressure plate step shaft 1203 provides a clear axial positioning boundary for the second active friction plate 16, the inner diameter of the second active friction plate 16 is slightly larger than the outer diameter of the pressure plate step shaft 1203, which ensures that the friction plate can rotate flexibly with the active component, and limits its excessive movement toward the pressure plate cover 1201 through the step surface, ensuring that the friction plate is stably distributed in the set position. 2, while achieving a circumferential rigid connection, it can move freely axially with the clutch action to avoid the friction plate from being unable to separate; the inner diameter of the second active friction plate 16 is slightly larger than the outer diameter of the pressure plate step shaft 1203, which reduces the processing accuracy requirements of the two and facilitates rapid insertion and assembly. The standardized cooperation of the internal spline of the second driven friction plate 17 and the keyway of the pressure plate transmission shaft segment 1202 can achieve rapid alignment through the guidance of the spline, shortening the assembly time and improving assembly efficiency; the clearance cooperation of the second active friction plate 16 and the pressure plate step shaft 1203 makes it have no direct contact friction with the surface of the shaft segment during rotation, and only transmits power through the joint surface with the second driven friction plate 17, avoiding energy loss and heat caused by contact wear between the shaft segment and the friction plate, reducing ineffective friction, and reducing operating energy consumption. It also has the characteristics of improving clutch response speed, facilitating local maintenance and replacement, and reducing use costs, which will not be repeated here.

[0035] In this embodiment, the hydraulic system includes a hydraulic cylinder body 15, which forms a hydraulic cylinder. A piston portion 1204 that cooperates with the hydraulic cylinder is formed on the pressure plate 12. The piston and the pressure plate in the traditional structure are usually independent components, and force needs to be transmitted through connecting parts such as bolts or push rods, which will increase the axial size and assembly level. In this embodiment, the piston portion 1204 and the pressure plate 12 are formed as one piece, eliminating the installation space and connection structure of the independent piston, shortening the overall axial length of the clutch, and making the overall structural layout more compact; when the hydraulic oil pushes the piston portion 1204, the thrust can directly act on the pressure plate 12, avoiding the force transmission loss between the independent piston and the pressure plate 12 due to the connection gap or elastic deformation, and reducing the action delay. , improving the control accuracy of the hydraulic system; the integrated design of the piston part 1204 and the pressure plate 12 can eliminate the weak points in the connection between the components, improve the overall anti-deformation ability, and stably transmit the axial force. The piston part 1204 and the pressure plate 12 reduce the sealing surface at the connection between the piston and the pressure plate in the traditional split structure, reducing the risk of hydraulic oil leakage. At the same time, the matching surface of the piston part 1204 and the hydraulic cylinder body 15 is easier to achieve precision machining, which is convenient for installing seals and further improving the sealing of the hydraulic system; a coil spring 11 is provided on the piston part 1204, and the coil spring 11 is fixed by an elastic retaining ring 8, a spring seat 9 and a spring support seat 10, which is a conventional means of the prior art, or the spring support seat 10 is not used, such as Figure 9 As shown, instead of designing a corresponding support structure on the center sleeve 2, the space utilization rate is improved; of course, the diameter of the piston portion 1204 can be increased, while reducing the volume of the hydraulic cylinder to improve the response performance of the clutch, as shown in FIG. Figure 7 As shown, no further details are given here.

[0036] In this embodiment, a main shaft 6 is also included. The hydraulic cylinder body 15 has a side wall 1501, a cylinder body center shaft sleeve 1502 and a bottom 1503. The cylinder body center shaft sleeve 1502 is outermost on the main shaft 6. The piston part 1204 is located between the side wall 1501 and the cylinder body center shaft sleeve 1502 and forms a sliding seal. The outer circle of the cylinder body 15 and the inner circle of the pressure plate transmission shaft section 1202 form a sliding seal. The piston part 1204 is located between the side wall 1501 and the cylinder body center shaft sleeve 1502 and forms a sliding seal, which can effectively prevent the hydraulic oil in the hydraulic cylinder from leaking to the main shaft 6, avoiding the overall pressure reduction caused by hydraulic oil leakage, the clutch cannot be normally tightened, and then the clutch fails. The sliding seal between the outer circle of the cylinder body 15 and the inner circle of the pressure plate transmission shaft section 1202 further prevents the hydraulic oil from leaking to the outside of the clutch, prevents insufficient hydraulic pressure due to oil loss, reduces the risk of hydraulic oil leakage, and ensures the stability of the hydraulic system pressure. The working reliability of the clutch is improved; the cylinder center sleeve 1502 is externally mounted on the main shaft 6, so that the hydraulic cylinder 15 and the main shaft 6 form a coaxial nested structure, avoiding the radial space conflict between the hydraulic system and the main shaft 6 in the traditional split design, reducing the overall radial size of the clutch, and also providing a radial positioning reference for the hydraulic cylinder 15 to ensure its coaxiality with the main shaft 6 and the pressure plate 12, avoiding the piston part 1204 from being stuck or the seal from being abnormally worn due to eccentricity. The double sliding seal allows the piston part 1204 to move smoothly in the axial direction with the hydraulic pressure, while ensuring the relative sliding accuracy between the pressure plate drive shaft section 1202 and the cylinder 15, so that the thrust of the pressure plate 12 can be evenly transmitted to the friction plate, reducing the problem of uneven engagement or / and separation caused by movement jamming, and improving the accuracy of the clutch action; the hydraulic cylinder 15 forms a frame structure through the side wall 1501, the bottom 1503 and the cylinder center sleeve 1502 to withstand the radial pressure of the hydraulic oil; Figure 1 As shown, the center sleeve 2 is outer-mounted on the main shaft 6 and fixed by a hexagonal nut 3. An oil seal 4 for preventing leakage of lubricating oil or entry of foreign matter and a bearing 5 for supporting the main shaft and reducing friction during operation are provided on the upper part of the main shaft 6. The piston portion 1204 is located between the side wall 1501 and the cylinder center sleeve 1502 and forms a sliding seal through a sealing ring 7. A sliding seal is formed between the outer circle of the cylinder 15 and the inner circle of the pressure plate transmission shaft section 1202 through the sealing ring 7. These are all conventional means of the prior art. Of course, the position of the piston portion 1204 can also be adjusted from the inner side of the hydraulic cylinder body 15 to the outer side of the hydraulic cylinder body 15, as shown in FIG. Figure 8 As shown, it also has the effect of improving space utilization, which will not be described here.

[0037] In this embodiment, a hydraulic oil passage 601 is provided on the main shaft 6, and the hydraulic cylinder is connected to the hydraulic oil passage 601 through the oil hole 1504 on the central shaft sleeve 1502 of the cylinder body. The hydraulic oil passage 601 is integrated into the interior of the main shaft 6, and the central axis space of the main shaft 6 is used as the hydraulic oil passage carrier, and the oil hole 1504 of the central shaft sleeve 1502 of the cylinder body is coordinated with the hydraulic cylinder to achieve communication with the hydraulic cylinder, so that the hydraulic oil passage is completely built into the main shaft 6 and the hydraulic cylinder body 15, avoiding the arrangement of external pipelines, reducing the radial and axial space occupied by the clutch, and improving space utilization; the hydraulic oil passage path goes directly from the inside of the main shaft 6 to the hydraulic cylinder, shortening the flow distance of the hydraulic oil, reducing The pressure loss caused by excessively long or curved pipelines is reduced, making the pressure transmission of the hydraulic system more direct and efficient. The integrated design of the hydraulic oil channel 601 and the main shaft 6 enables the main shaft to not only assume the transmission function but also serve as an oil channel carrier, thus realizing the structural integration of power transmission and hydraulic control. At the same time, the oil hole 1504 of the cylinder center shaft sleeve 1502 serves as a connection node, organically connecting the main shaft 6, the hydraulic cylinder 15, the pressure plate 12 and other components through the hydraulic oil channel, thereby improving the overall structural coordination and functional integration of the clutch. The main shaft 6 is also provided with a lubricating oil channel 602 for conveying lubricating oil, which is a conventional means in the prior art and will not be described in detail here.

[0038] The piston part 1204 is provided with an annular groove 1205, and the side wall 1501 of the hydraulic cylinder body is located in the annular groove 1205 and forms a sliding seal with the outer wall of the annular groove 1205. The annular groove 1205 provides a stable installation slot for the seal to avoid displacement or extrusion under high pressure, thereby extending the service life of the seal. At the same time, the outer wall of the annular groove 1205 can prevent external impurities from invading the sealing area, thereby reducing seal wear; the cooperation between the annular groove 1205 and the side wall 1501 provides precise radial positioning for the piston part 1204, ensuring that it slides smoothly in the axial direction in the hydraulic cylinder, avoiding unilateral force unevenness caused by eccentricity, and reducing friction plate wear and abnormal noise problems; the annular groove 1205 and the side wall 1501 provide ... The annular groove 1205 can serve as a buffer chamber for the hydraulic oil. When the piston part 1204 moves rapidly, the hydraulic oil in the annular groove 1205 can achieve flow compensation through the tiny gap between the side wall 1501 and the outer wall of the annular groove 1205, thereby reducing pressure shock and cavitation, making the pressure change of the hydraulic system smoother, and improving the smoothness of the clutch action. In the existing design, the sealing structure of the piston and the cylinder body requires additional axial space, such as a sealing groove or a guide ring, etc., while this embodiment integrates the sealing function and structural positioning in the same axial position through the nested cooperation of the annular groove 1205 and the side wall 1501, shortening the axial length of the piston part 1204 and making the overall layout of the clutch more compact.

[0039] In this embodiment, the pressure plate 12 is located around the piston portion 1204 to form an axial group portion 1206, and the center sleeve transmission shaft section 202 is sleeved on the axial group portion 1206. The axial group portion 1206 serves as an axial extension structure of the pressure plate 12, which improves the ability to resist deformation, avoids the pressure plate 12 from warping or bending due to excessive local force, and ensures that the friction plate is uniformly stressed; the center sleeve transmission shaft section 202 sleeved on the axial group portion 1206 forms a radial constraint on the pressure plate 12, limits its radial shaking during high-speed rotation or frequent clutching, reduces the eccentric wear and noise of the friction plate caused by vibration, and improves the stability of system operation; the internal and external nested structure of the axial group portion 1206 and the center sleeve transmission shaft section 202 makes full use of the internal The annular space avoids the side-by-side arrangement or axial stacking of components in traditional designs, significantly reducing the radial size of the clutch; the direct cooperation between the shaft-shaped group 1206 and the center sleeve transmission shaft segment 202 allows the torque to be transmitted from the active component to the driven component through a shorter path, reducing the energy loss in the intermediate links and improving the transmission efficiency. The multiple shafts of the shaft-shaped group 1206 form a larger contact area with the inner surface of the center sleeve transmission shaft segment 202, and can transmit greater torque through key connection, spline fitting or interference fitting in the existing technology. Of course, the pressure plate 12 can also form splines around the piston part 1204, and the center sleeve transmission shaft segment 202 cooperates with the splines around the piston part 1204 to achieve similar effects, which will not be repeated here.

[0040] The end of the pressure plate transmission shaft section 1202 is provided with a pressure plate annular groove 1207, and the center sleeve transmission shaft section 202 extends into the pressure plate annular groove 1207, forming a nested structure in the groove, and the inner side wall and the outer side wall of the pressure plate annular groove 1207 can form an axial limit for the center sleeve transmission shaft section 202, limit the excessive relative displacement of the two in the axial direction, avoid component collision, abnormal noise or friction plate misalignment caused by axial movement, and ensure movement accuracy; the nested design of the center sleeve transmission shaft section 202 extending into the pressure plate annular groove 1207 can be used to allow the pressure plate transmission shaft sections 1202 that originally need to be arranged axially side by side to be It partially overlaps with the center sleeve transmission shaft section 202, reducing the overall axial space occupied; the pressure plate annular groove 1207 provides an accommodating space for the center sleeve transmission shaft section 202, which can avoid structural interference between the two during axial movement, and at the same time, no additional avoidance gap is required, thereby improving space utilization; the opening of the pressure plate annular groove 1207 can make the end structure of the pressure plate transmission shaft section 1202 more evenly distribute the load, avoid stress concentration on the end edge, and reduce the risk of cracking; of course, the pressure plate 12 can also be externally mounted on the center sleeve 2, and the pressure plate 12 is provided with a spline or annular groove, and the center sleeve 2 is provided with a corresponding spline or stepped shaft, which can also achieve the above functions and will not be repeated here.

[0041] The motorcycle of this embodiment includes the hydraulic clutch, including an outer cover 1, a center sleeve 2, a pressure plate 12, an active friction plate, a driven friction plate and a hydraulic system. The active friction plate and the driven friction plate are distributed on the outer circumference of the center sleeve 2 and / or the pressure plate 12. The inner diameters of some active friction plates and driven friction plates are different to adapt to the different radial dimensions of the center sleeve 2 and / or the pressure plate 12. The first active friction plate 13 is distributed axially corresponding to the center sleeve 2, and the second active friction plate 16 is distributed axially corresponding to the pressure plate 12. It can control the load-bearing torque of the clutch and accurately control the clutch according to the requirements of different working conditions; an axial group portion 1206 is formed around the piston portion 1204 formed on the pressure plate 12, and the center sleeve transmission shaft section 202 is outermostly arranged on the axial group portion 1206. A pressure plate annular groove 1207 is provided at the end of the pressure plate transmission shaft section 1202, and the center sleeve transmission shaft section 202 extends into the pressure plate annular groove 1207, which not only enhances the connection strength, but also reduces the overall volume, thereby achieving the purpose of compact structure and having higher economy.

[0042] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and are not limiting. Although the present invention has been described in detail with reference to the preferred embodiments, those skilled in the art should understand that the technical solutions of the present invention may be modified or replaced by equivalents without departing from the purpose and scope of the technical solutions of the present invention, which should all be included in the scope of the claims of the present invention.

Claims

1. A hydraulic clutch, characterized in that: It includes an outer cover, a center sleeve, a pressure plate, a plurality of active friction plates, a plurality of driven friction plates and a hydraulic system. The active friction plates and the driven friction plates are distributed on the outer circumference of the corresponding positions of the center sleeve and / or the pressure plate. The inner diameters of the active friction plates are respectively adapted to the radial dimensions of the corresponding positions of the center sleeve and / or the pressure plate, so that the inner diameters of the several active friction plates are different; the inner diameters of the driven friction plates are respectively adapted to the radial dimensions of the corresponding positions of the center sleeve and / or the pressure plate, so that the inner diameters of the several driven friction plates are different.

2. The hydraulic clutch according to claim 1, characterized in that: The active friction plates include several first active friction plates and several second active friction plates. The first active friction plates are distributed axially corresponding to the center sleeve, and the second active friction plates are distributed axially corresponding to the pressure plate. The inner diameters of the first active friction plates and the second active friction plates are different.

3. The hydraulic clutch according to claim 1, characterized in that: The driven friction plates include a plurality of first driven friction plates and a plurality of second driven friction plates. The first driven friction plates are axially distributed corresponding to the center sleeve and are matched with the center sleeve for transmission. The second driven friction plates are axially distributed corresponding to the pressure plate and are matched with the pressure plate for transmission. The inner diameters of the first driven friction plates and the second driven friction plates are different.

4. The hydraulic clutch according to claim 2 or 3, characterized in that: The center sleeve includes a center sleeve cover and a center sleeve transmission shaft section, a center sleeve step shaft is formed between the center sleeve cover and the center sleeve transmission shaft section, the inner diameter of the first active friction plate is slightly larger than the outer diameter of the center sleeve step shaft, and the first driven friction plate has an internal spline and cooperates with the keyway of the center sleeve transmission shaft section through the internal spline.

5. The hydraulic clutch according to claim 2 or 3, characterized in that: The pressure plate includes a pressure plate cover and a pressure plate transmission shaft section, a pressure plate step shaft is formed between the pressure plate cover and the pressure plate transmission shaft section, the inner diameter of the second active friction plate is slightly larger than the outer diameter of the pressure plate step shaft, and the second driven friction plate has an internal spline and cooperates with the keyway of the pressure plate transmission shaft section through the internal spline.

6. The hydraulic clutch according to claim 1, characterized in that: The hydraulic system includes a hydraulic cylinder body, the hydraulic cylinder body forms a hydraulic cylinder, and a piston portion cooperating with the hydraulic cylinder is formed on the pressure plate.

7. The hydraulic clutch according to claim 6, characterized in that: It also includes a main shaft, the hydraulic cylinder body has a side wall, a cylinder body center sleeve and a bottom, the cylinder body center sleeve is outermost on the main shaft, the piston part is located between the side wall and the cylinder body center sleeve and forms a sliding seal, and a sliding seal is formed between the outer circle of the cylinder body and the inner circle of the pressure plate transmission shaft section.

8. The hydraulic clutch according to claim 7, characterized in that: A hydraulic oil passage is provided on the main shaft, and the hydraulic cylinder is connected to the hydraulic oil passage through an oil hole on the central shaft sleeve of the cylinder body; The piston portion is provided with an annular groove, and the side wall of the hydraulic cylinder body is located in the annular groove and forms a sliding seal with the outer wall of the annular groove.

9. The hydraulic clutch according to claim 8, characterized in that: The pressure plate is located around the piston portion to form a shaft-shaped group of parts, and the center sleeve transmission shaft section is externally mounted on the shaft-shaped group of parts; A pressing plate annular groove is formed at the end of the pressing plate transmission shaft section, and the center sleeve transmission shaft section extends into the pressing plate annular groove.

10. A motorcycle, characterized in that: Including the hydraulic clutch according to any one of claims 1-9.

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